Downhole pump with standing valve assembly which guides the ball off-center

ABSTRACT

Disclosed is a standing valve containing a ball, in which during operation, the ball is moved by ball guides to a position off center and yet not impinged against the valve, and in which unequal fluid flow areas are created around the horizontal circumference of the ball. Further disclosed are pumps utilizing such a standing valve.

RELATED APPLICATION DATA

This application is a Continuation-In-Part application of U.S. patentapplication Ser. No. 08/784,600 filed Jan. 21, 1997 which is aContinuation in Part of Ser. No. 08/625,205, filed Apr. 1, 1996 nowissued as U.S. Pat. No. 5,628,624.

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates to valves and pumps. In another aspect,the present invention relates to ball and seat valves, and to pumpsutilizing said valves. In even another aspect, the present inventionrelates to ball and seat valves utilizing a piston mechanism to unseatthe ball from the seat, and to downhole pumps utilizing said valves. Instill another embodiment, the present invention relates to a standingvalve, and to pumps utilizing such valves. In yet another aspect, thepresent invention relates to a standing valve in which guides urge theball off center, and to pumps utilizing such valves.

2. Description of the Related Art

In the production of hydrocarbons from subterranean formations, it isdesirable that the pressure of the formation "produce" or force thehydrocarbons to the surface. Unfortunately, sometimes formation pressuremay be initially too low to produce the formation, or may decline tothat point as hydrocarbons are produced from a formation. Resort mustthen be made to the use of a pump to produce the formation.

Most commonly in petroleum production technology, producing wellsutilize a so called "sucker rod" to lift oil from subterraneanformations to the surface of the earth. Sucker rod pumps are generallyeither a rod pump or a tubing pump. Tubing pumps are constructed suchthat the barrel assembly is an integral part of the tubing string andsuch that the plunger assembly is part of the rod string. Rod pumps,however, are of the stationary barrel traveling plunger type, whereinthe barrel assembly is wedged into the seating nipple at the bottom ofthe tubing, thus providing a seal point.

In general a sucker rod pump is a reciprocating pump which is normallysecured to the lowermost end of the sucker rod string, which extendslongitudinally through the well bore from a reciprocating device at thesurface of the ground. The reciprocating device at the surface isusually a horsehead type apparatus and alternatively raises and lowers astring of sucker rods in the well bore.

The sucker rod pump itself generally includes a housing through which apiston is reciprocated by the sucker rod linkage. In its simplest form,the pump usually includes a number of ball and seat valves with one suchvalve in the piston and another at the inlet port of the housing. On theupstroke of the plunger, the ball in the inlet port valve ("standingvalve") is drawn away from its seat and the ball of the outlet portvalve ("traveling valve") is forced over its seat to draw fluid frombelow the seating nipple and into the housing. On the piston'sdownstroke, the ball in the standing valve is forced into its seat andthe ball in the traveling valve moves away from its seat to allow thepiston to move downwardly through the fluid contained in the housing. Onthe subsequent upstroke, the closing of the traveling valve forces thefluid above the piston, out of the housing through the outlet ports andinto the tubing above the pump and simultaneously fills the housingbelow the piston with fluid. Repetition of this cycle eventually fillsthe tubing string and causes the fluid to flow to the surface.

One problem encountered by sucker rod pumps is caused by the wear of theball and seat valves. The fluid produced from many geological formationscontains minute, abrasive particles, such as sand, which lodge betweenthe ball and seat and wear away the valve components. Over a period oftime, the sealing efficiency of the valves is reduced to such an extentthat the pump must be removed and repaired or replaced. In some wells,where the production fluid is particularly sandy or corrosive, thesepumps must be replaced at frequent intervals. It is, of course, evidentthat removing and repairing or replacing a pump, and the associatedlosses of lost production time during the repair or replacement process,can be significant expense factors.

Another problem associated with such conventional ball and valvesub-surface oilfield pumps is generally known as "gas locking". In suchpumps, the fluid head pressure in the tubing string is held by thetraveling valve, on the upstroke of the piston, and by the lowerstanding valve on the downstroke of the piston. The down stroke of thetraveling valve builds up pressure on the fluid between the travelingvalve and the standing valve which causes the traveling valve to open toallow fluid to pass above the traveling valve. However, in a wellproducing both oil and gas, the chamber between the traveling valve andthe standing valve, frequently fills with gas, and due to thecompressibility of gas, the downstroke of the traveling valve may notbuild up sufficient pressure in the chamber below the traveling valve toact upwardly on the ball of the traveling valve to overcome the immensepressure of the fluid column above the traveling valve which actsdownwardly on the ball of the traveling valve, resulting in the ball ofthe traveling valve remaining in the closed seated position during thedownstroke. Thus, the gas between the standing valve and the travelingvalve merely compresses and expands with each stroke of the pump,producing the operational failure of the pump known as "gas locking".This condition may remedy itself after a short time or may continueindefinitely.

Even another problem associated with such conventional ball and valvesub-surface oilfield pumps is generally known as "fluid pounding." Thisfluid pounding occurs when the pump does not fill completely with liquidduring the upstroke, resulting in the formation of a low pressure gascap in the top of the pump chamber between the traveling valve and thestanding valve. During the subsequent downstroke the traveling valvestays closed until it impacts the fluid.

There has been a long felt need to solve the above described problemsassociated with such conventional ball and valve sub-surface oilfieldpumps, and the art is replete with attempts to solve one or more of theabove problems.

U.S. Pat. No. 1,585,544, issued May 18, 1926 to Hubbard, discusses theproblem of "air hammering", and suggests the use of a rod mounted on thestanding valve which impacts the ball of the traveling valve as thetraveling valve is moved toward the standing valve. However, given theexpansion and contraction of the sucker rods, the traveling valve maynot reach the rod, or may extend past the rod, damaging the valve.

U.S. Pat. No. 4,691,735, issued Sep. 8, 1987 to Horton, discloses atraveling valve for an oil well pump, which includes a piston below thetraveling valve which lifts the traveling valve ball above the travelingvalve seat. On the downstroke, pressure builds up between the standingvalve and the piston, to force the piston upward to lift the ball.However, since the piston cross-sectional area affected by the pressurebetween the standing valve and the piston is equal to thecross-sectional area of the traveling valve seat, no mechanicaladvantage is provided by the arrangement of Horton. Thus, Horton suffersfrom "gas locking" to the same extent as conventional traveling valves.Additionally, the Horton traveling valve and the rod assembly are notmounted below the bottom of the plunger, and thus must be made ofmaterials strong enough to withstand the rigors of operation of thepump.

U.S. Pat. No. 4,781,547, issued Nov. 1, 1988 to Madden, discloses apushrod assembly mounted below the traveling valve, which pushrod isalternatively moved from an extended into a retracted position eachupstroke and downstroke of the pump. The free terminal end of thepushrod is arranged to engage the traveling valve ball as the pumpcommences the downstroke. However, since the bottom of the pushrodincludes several channels, pressure does not build up between thepushrod and the standing valve during the downstroke. Rather, during thedownstroke liquid is forced through the channels in the bottom of thepushrod. Movement of the pushrod is affected by inertia, pressuredifferential of the liquid flow through the channels, and frictionbetween the pushrod and the pump barrel.

Therefore, there is a need in the art for an improved downholereciprocating pump.

There is another need in the art for an improved apparatus for movingthe traveling valve ball during the downstroke of a downholereciprocating pump.

These and other needs in the art will become apparent to those of skillin the art upon review of this patent specification, claims anddrawings.

SUMMARY OF THE INVENTION

It is an object of the present invention to provide an improved downholereciprocating pump.

It is another object of the present invention to provide for an improvedapparatus for moving the traveling valve ball during the downstroke of adownhole reciprocating pump.

These and other objects of the present invention will become apparent tothose of skill in the art upon review of this patent specification,claims and drawings.

According to one embodiment of the present invention there is provided aball and seat valve assembly which generally includes a hollow tubularmember holding a ball and valve. Mounted within the tubular member bybelow valve seat is a piston with an actuator for engaging the seatedball. Mechanical advantage is provided either by providing a sealingarea of the piston that is greater than the sealing area of the seatvalve and/or by providing an actuator suitable to strike the seated ballasymmetrically with respect to the vertical axis through the center lineof the ball. Surface indentations or extensions are provided along thesurface of the piston to urge rotation of the piston as it travels.

According to another embodiment of the present invention there isprovided a ball and seat assembly which generally includes a ball andseat valve. Mounted to the bottom of the valve is a tubular memberhaving therein a piston with an actuator for engaging the seated ball.Mechanical advantage is provided either by providing a sealing area ofthe piston that is greater than the sealing area of the seat valveand/or by providing an actuator suitable to strike the seated ballasymmetrically with respect to the vertical axis through the center lineof the ball. Surface indentations or extensions are provided along thesurface of the piston to urge rotation of the piston as it travels.

According to even another embodiment of the present invention there isprovided a ball and seat assembly which generally includes a firsttubular member containing a ball and seat valve. Mounted to the bottomof the first tubular member is a second tubular member having therein apiston with an actuator for engaging the seated ball. Mechanicaladvantage is provided either by providing a sealing area of the pistonthat is greater than the sealing area of the seat valve and/or byproviding an actuator suitable to strike the seated ball asymmetricallywith respect to the vertical axis through the center line of the ball.Surface indentations or extensions are provided along the surface of thepiston to urge rotation of the piston as it travels.

According to still another embodiment of the present invention there isprovided a pump assembly which generally includes a pump housing with amovable barrel positioned therein. Affixed to the barrel is a travelingball and seat valve. Mounted to the bottom of barrel is a tubular memberhaving therein a piston with an actuator for engaging the seated ball.Mechanical advantage is provided either by providing a sealing area ofthe piston that is greater than the sealing area of the seat valveand/or by providing an actuator suitable to strike the seated ballasymmetrically with respect to the vertical axis through the center lineof the ball. Surface indentations or extensions are provided along thesurface of the piston to urge rotation of the piston as it travels.

According to yet another embodiment of the present invention there isprovided a standing valve, which can be utilized with the abovedescribed pumps, in which the ball valve is moved off center by one ormore guides to a position that is both off center of the standing valveyet not impinging on the side of the standing valve, and in whichunequal liquid flow areas are created around the horizontalcircumference of the ball.

BRIEF DESCRIPTION OF THE DRAWINGS

FIGS. 1A, 1B and 1C are cross-sectional views of reciprocating fluidpump 10 of the present invention showing piston 40 in a lower,intermediate and upper position, respectively.

FIGS. 2 and 3 are horizontal cross-sectional views taken along FIG. 1lines 2--2 and 3--3, respectively, of reciprocating fluid pump 10 of thepresent invention.

FIGS. 4A and 4B are isometric views of piston 40 of the presentinvention, which is utilized for moving the ball from the travelingvalve.

FIG. 5 shows pump 10 of FIG. 1 except that for piston 40, actuator 41shown in FIG. 1 has been replaced by actuator 141.

FIG. 6 shows pump 10 of FIG. 1 except that for piston 40, actuator 41shown in FIG. 1 has been replaced by actuator 241 as shown in FIG. 5.

FIG. 7A an FIG. 7B is an isometric view of piston 40 with actuator 241.

FIGS. 8 and 9 are top and side views, respectively, of end 241A ofactuator 241, showing top end 245, striking face 243.

FIG. 10 shows pump 10 of FIG. 1, except that an upper sealing member 38without flow areas 79 is utilized, and except that upper stops 55 havebeen replaced by upper stops 55A of housing 27.

FIG. 11 is a horizontal cross-sectional view taken along FIG. 10 lines11--11, of reciprocating fluid pump 10 of the present invention.

FIG. 12 shows pump 10 further having a weight system 300, which is usedto further urge piston 40 from its upper to its lower position.

FIG. 13 is a view of weight 305 of FIG. 12, taken along FIG. 12 line13--13, showing weight sections 305A and 305B connected around couplingend 302A.

FIG. 14 is a view of pump 10, with channels 62 modified to allow forproduction of heavy crude oils.

FIG. 15 is a horizontal cross-sectional view taken along FIG. 14 line15--15, of reciprocating fluid pump 10 of the present invention.

FIG. 16 is a view of weight/plunger system 300 showing fluid outlet307C.

FIG. 17A is a view of weight/plunger 305 taken alnong FIG. 16 line17A--17A showing spiral groove connector 302B, flow channels 310, fluidentrance 310A and fluid exit 310B.

FIG. 17B is a view of weight/plunger 305 taken along FIG. 16 line17B--17B, showing weight/plunger 305 having sections 305A and 305B.

FIG. 18 is a view of pump 10 with actuator piston body 42A modified withradial fins.

FIG. 19A and FIG. 19B are an isometric view of piston 40 with actuatorpiston body 42A and reinforcement for upper valve 42B.

FIG. 20 is a cross-sectional view of reciprocating fluid pump 10 of thepresent invention showing new standing valve 58A with conventional ball56 and conventional seat 57.

FIG. 21 is a cross-sectional view of standing valve 58A taken along FIG.20 line 21--21.

FIG. 22 is a cross-sectional view of standing valve 58A taken along FIG.20 line 22--22.

FIG. 23 is a cross-sectional view of standing valve 58A taken along FIG.20 line 23--23.

FIG. 24 is a cross-sectional view of standing valve 58A showingremovable liner.

DETAILED DESCRIPTION OF THE INVENTION

Referring now to FIGS. 1A, 1B, 1C, 2, 3, 4A and 4B there is shown oneembodiment of the present invention.

FIGS. 1A, 1B and 1C are cross-sectional views of reciprocating fluidpump 10 of the present invention showing piston 40 in a lower,intermediate and upper position, respectively.

FIGS. 2 and 3 are horizontal cross-sectional views taken along line 2--2and 3--3, respectively, of reciprocating fluid pump 10 of the presentinvention.

FIGS. 4A and 4B are isometric views of piston 40 of the presentinvention, which is utilized for moving the ball from the travelingvalve.

Conventional sucker/pump rod 12 connects to reciprocating fluid pump 10of the present invention via threaded connection to conventional plungerconnector 15, which is in turn connected via threaded connection toconventional plunger 18, which is in turn connected via threadedconnection to conventional traveling valve cage 21 of traveling valve 70having seat 78 and ball 75, all of which is encased in conventionalbarrel 23.

It is to be understood that conventional sucker/pump rod 12 is actuatedfrom the surface by any of the well known means, usually a "rockinghorse" type pumpjack unit.

Threaded connection 25 joins traveling valve cage 21 with tubularhousing 27, which extends downwardly to lower housing 29 by threadedconnector 31. Housing 29 in turn extends downwardly and connects tohousing 33 through threaded connector 35. It is to be understood thathousings 27, 29 and 33 form hollow tubular housing assembly 5 of thepresent invention which is adapted for attachment to the traveling valve70. While assembly 5 is illustrated as having three housings 27, 29 and33, it is to be understood that the number of housings utilized is notcritical, and that one or more housings can be utilized. Generallyhowever, at least two housings are utilized to allow for easierinsertion of piston 40 into housing assembly 5.

At the bottom of barrel 23 is positioned conventional standing valve 58,including conventional seat 57 and ball 56.

Piston 40 is positioned within tubular assembly 5 within pump 10 asshown, and includes actuator 41 having engaging end 41A, lower sealingmember 36, upper sealing member 38, piston body 42.

The vertical motion of piston 40 in housing assembly 5 within pump 10 isrestricted at its uppermost point by the engagement of upper stops 55 ofhousing 27 and shoulders 32 of upper sealing member 38 as shown in FIG.1C, and at its lowermost point by engagement of lower stops 54 ofhousing 33 with bottom shoulder 36A of lower sealing member 36 as shownin FIG. 1A.

Liquid flow around lower sealing member 36 through channels 62 inhousing 29 occurs once bottom shoulder 36A clears lower end 62A ofchannels 62. In the embodiment as shown in FIG. 3 channels 62 are notcontinuously connected around the perimeter of housing 29, but ratherare spaced by guides 64 formed in the walls of housing 29. While threechannels 62 are utilized in the embodiment of pump 10 shown, it is to beunderstood that any number of channels 62 may be utilized, as long as atleast one channel 62 is provided. Thus, when bottom shoulder 36A isabove lower channel end 62A, lower sealing member 36 is positioned inlower housing 29 by guides 64.

Liquid flow around sealing member 36 is prevented when bottom shouldermember 36A is positioned below lower channel member 62A. Sealing member36 will form a seal with lower housing 29 such that pressure can be heldby sealing member 36. Additional optional sealing can be provided byutilizing a sealing seat against which sealing member 36 will abut. Inthe embodiment shown in FIG. 1A, lower stop 54 is additionally a sealseat for sealing member 36. Thus, sealing is provided by sealing member36 circumferentially abutting housing 29, and by the bottom of sealingmember 36 abutting lower stop or seat 54.

Lower sealing member 36 includes sealing area 71 which may be any shapesuitable to seal the internal cross-section of housing 29 below channelend 62A. In the embodiment shown, sealing area 71 is a concave shape,although any suitable shape may be utilized.

It is to be understood that in the event of fluid leakage past orfailure of traveling valve 70, sealing member 36 may be designedsuitable to provide backup sealing. It is also possible to eliminatetraveling valve 70, and utilize sealing member 36 as the primarytraveling valve.

Liquid flow around upper sealing member 38 through channels 67 inhousing 27 occurs once bottom shoulder 38A clears lower end 67A ofchannels 67. In the embodiment as shown in FIG. 2 channels 67 are notcontinuously connected around the perimeter of housing 27, but ratherare spaced by guides 69 formed in the walls of housing 27. While threechannels 67 are utilized in the embodiment of pump 10 shown, it is to beunderstood that any number of channels 67 may be utilized, as long as atleast one channel 67 is provided. Thus, when bottom shoulder 38A isabove lower channel end 67A, lower sealing member 38 is positioned inhousing 27 by guides 69.

With piston 40 at its uppermost point, with upper stops 55 of housing 27and shoulders 32 of upper sealing member 38 in engagement, liquid flowwill still occur around sealing member 38. Flow area 79 extendsdownwardly along the side of sealing member 38 as shown in FIGS. 4A and4B to form a liquid passage with channel 67. Even when shoulder 32 isabutted against stop 55 this flow area 79 is in liquid communicationwith channel 67, and thus allows for passage of fluid from channel 67and past sealing member 38 through flow area 79.

Liquid flow around sealing member 38 is prevented when bottom shouldermember 38A is positioned below lower channel member 67A. Sealing member38 will form a seal with housing 27 such that pressure can be held bysealing member 38.

Sealing member 38 includes sealing area 74 which may be any shapesuitable to seal the internal cross-section of housing 27 below channelend 67A. In the embodiment shown, sealing area 74 is a concave shape,although any suitable shape may be utilized.

This embodiment of the present invention is illustrated with two sealingmembers 36 and 38. It is to be understood that at the very least, onesealing member must be utilized, with additional sealing members beingoptional. However, one problem that must be addressed is the orientationof the piston 40. While one sealing member could be modified to keeppiston 40 in its proper vertical alignment, it is preferred to utilizeeither a second sealing member, or a rod guide to keep piston 40 alignedproperly.

It is important that the sealing area of the sealing member that holdspressure against standing valve 58, which in the embodiment shown issealing area 71 of member 36 initially, and subsequently sealing area 74of member 38, have a sealing area that is greater than thecross-sectional area of valve seat passage 78B. Preferably, the sealingarea of sealing member 36 and/or 38 will be at least 1.1 times greaterthan the cross-sectional area of valve seat passage 78B, more preferablyat least 2 times greater, even more preferably at least 5 times greater,even still more preferably at least 6 times greater, even yet morepreferably at least 9 times greater, and most preferably at least 12times greater.

While not wishing to be limited by theory, the inventor believes thatthe greater sealing area of sealing area 71 of member 36 or sealing area74 of member 38 will provide a mechanical advantage over pressuring theseat alone as follows. Pressure acting on the seat alone will provide aforce equal to the product of the pressure and the cross-sectional areaof the seat. Pressure acting upon sealing area 71 of member 36 orsealing area 74 of member 38 will provide a force equal to the productof the pressure and the area of sealing area 71 or sealing area 74.Having a greater sealing area 71 or 74 for member 36 or 38 will providea mechanical advantage for overcoming the fluid column force actingdownwardly upon ball 75, requiring less pressure on sealing area 71 ofmember 36 or sealing area 74 of member 38 to ultimately unseat ball 75.

Operation of pump 10 is as follows. In the upstroke, sucker rod 12driven by a surface pumping unit moves plunger 18, traveling cage 21 andtubular assembly 5 upward. This motion closes traveling valve 70, forcespiston 40 into its downward position with shoulder 36A abutted againststop 54, and opens standing valve 58 and pulls liquid into conical area61 of pump 10. On the downstroke, plunger 18, traveling cage 21 andtubular assembly 5 are driven downward thereby closing standing valve 58and compressing the liquid drawn into area 61 between lower sealingmember 36 and the now closed standing valve 58, see FIG. 1A. With thecontinuing downstroke, this pressure builds and acts upon sealingsurface 71 of piston 40, ultimately driving it upward. Once shoulder 36Aclears channel bottom 62A liquid flow bypasses sealing member 36 bypassing through channel 62, see FIG. 1B. With piston 40 in thisintermediate position, pressure is now being held by sealing member 38.With the continuing downstroke, this pressure builds and acts uponsealing surface 74 of piston 40, ultimately driving it upward. Onceshoulder 38A clears channel bottom 67A, liquid flow goes around sealingmember 38 through channels 67, and on through traveling valve 70. Piston40 is ultimately driven to its upmost position with shoulder 32 ofmember 38 abutting stop 55, see FIG. 1C. At this point, liquid willcontinue to bypass sealing members 36 and 38 through channels 62 and 67,respectively, and on through traveling valve 70. This cycle is repeatedwith subsequent downstrokes and upstrokes.

Referring again to FIGS. 2 and 3 and additionally to FIG. 5, there isshown another embodiment of the present invention. The description forFIG. 1 above is applicable to FIG. 5 for like member numbers. FIG. 5shows pump 10 of FIG. 1 except that for piston 40, actuator 41 shown inFIG. 1 has been replaced by actuator 141 as shown in FIG. 5. Instead ofstriking seated traveling valve ball 75 near its vertical center axis,actuator 141 will strike traveling valve ball 75 in a position off ofits center axis as it is in its seated position. More specifically,actuator 141 must strike ball 75 to allow it to pivot on seat 78 atpivot point 78P. Even more specifically, actuator 141 will striketraveling valve ball 75 asymmetrically with respect to its verticalcenter axis as it is in its seated position. Such an asymmetricalstriking will create a moment with respect to the vertical center axiscausing ball 75 to pivot on seat 78 at pivot point 78P. With actuator141, this asymmetrical striking is achieved by angling member 141.

While not wishing to be limited to theory, the inventor believes thatthis asymmetrical striking will create a moment that will allow the ball75 to pivot on its seat 78 at point 78P. The inventor believes that thispivoting or prying action provides a mechanical advantage over merelyforcing ball 75 in the vertical direction that will help to overcome theliquid column pressure acting downwardly on ball 75.

Referring again to FIGS. 2 and 3 and additionally to FIGS. 6, 7A, 7B and8, there is shown even another embodiment of the present invention. Thedescription above is applicable to FIGS. 6, 7A, 7B and 8, for likenumbers. FIG. 6 shows pump 10 of FIG. 1 except that for piston 40,actuator 41 shown in FIG. 1 has been replaced by actuator 241 as shownin FIG. 6. FIG. 7A and FIG. 7B is an isometric view of piston 40 withactuator 241. FIGS. 8 and 9 are top and side views, respectively, of end241A of actuator 241, showing top end 245, striking face 243.

Like the embodiment shown in FIG. 5, this embodiment utilizes anasymmetrically striking of ball 75. In this embodiment however, thisasymmetrical striking is achieved by an actuator 241 that is offset fromthe vertical center line of pump 10.

Actuator 241 also employs a striking face 243 that is not only angledwith respect to the vertical plane, it also is pitched with respect tothe lateral plane. While not wishing to be limited by theory, theinventor believes that this angled and pitched striking face 243provides additional prying or leveraging action to help unseat ball 75from seat 78.

Referring now to FIGS. 10 and 11, there is shown still anotherembodiment of the present invention. The description above is applicableto FIGS. 10 and 11 for like numbers. FIG. 10 shows pump 10 of FIG. 1above, except that an upper sealing member 38 without flow areas 79 isutilized, and except that upper stops 55 have been replaced by upperstops 55A of housing 27.

Referring now to FIGS. 12 and 13, there is shown still anotherembodiment of the present invention. The description above is applicableto FIGS. 12 and 13 for like numbers. Additionally, FIG. 12 showsweight/plunger system 300, which is used to further encourage themovement of piston 40, by gravity, and downward by frictional dragduring the upstroke of the pump and upward by frictional drag during thedownstroke of the pump. At the very least, weight system 300 willinclude a weight/plunger 305 which is coupled to piston 40. Thisweight/plunger 305, which may be of any suitable shape to form africtional fit with the wall of the pump barrel, and includes one ormore channels 310 which allow fluid to by-pass weight/plunger 305. Inthe embodiment shown in FIG. 12, weight/plunger system 300 includes aconnector 302, which joins piston 40 with plunger/weight 305. Couplingend 302A of connector 302 is held within chamber 307 of weight 305, withconnector 302 extending through passage 307A of chamber 307. Chamber 307is oversized with respect to coupling end 302A to allow relativemovement between weight 305 and coupling end 302A. This relativemovement between weight 305 and coupling end 302A absorbs some of theshock of the movement of piston 40. It is to be understood, thatconnector 302 could also be made with some flexibility to absorb some ofthis shock.

Referring now to FIG. 13, there is shown a view of weight/plunger 305 ofFIG. 12, taken along FIG. 12 line 13--13. As shown in FIG. 13, weight305 includes sections 305A and 305B, which are connected around couplingend 302A. Weight/plunger 305 fits within the pump housing, with one ormore passages 310 along the side of weight/plunger 305, or alternativelythrough weight/plunger 305, allowing fluid to flow past weight/plunger305.

While weight/plunger system 300 is shown in conjunction with piston 40having modified upper sealing member 38, it is to be understood thatweight/plunger system 300 may be utilized with any type of piston 40.

Referring now to FIGS. 14 and 15, there is shown still anotherembodiment of the present invention. The description above is applicableto FIGS. 14 and 15 for like numbers. When producing heavier crude oils,it is sometime necessary to modify pump 10 to allow for flow aroundupper sealing member 38 and lower sealing member 36. This may beaccomplished by increasing the flow areas of channels 62 and/or 67.Additionally, with heavy crudes, it is sometimes also necessary to allowthe heavy crude to by-pass lower sealing member 36, even when it is inits lowermost position abutted against lower stop 54. This can beaccomplished by providing a channel, or modifying existing channels, toallow the heavy crude to by-pass lower sealing member 36 when abuttedagainst lower stop 54. For example, as shown in the embodiment of FIGS.14 and 15, the housing wall previously shown at 62W, has been removed towiden channel 62, and allow crude to by-pass lower sealing member 36when abutted against lower stop 54.

According to another embodiment of the present invention there isprovided apparatus for inducing, causing, biasing or urging rotation ofpiston 40 which apparatus may include helically aligned surfaceindentations such as grooves, slots, troughs, threads or channels,and/or surface extensions such as fins, baffles, nubs, tabs, or threads.It is to be understood that such apparatus may be positioned anywherealong piston 40, including on the actuator 41, actuator piston body 42,and/or weight/plunger system 300.

An illustration of such fins or baffles is shown in FIG. 18, 19A and19B. The description above is applicable to FIGS. 18, 19A and 19B forlike numbers. Referring to FIG. 18, there is shown a view of pump 10except that the actuator piston body 42 has been replaced by actuatorpiston body 42A. Instead of being smooth, actuator piston body 42Acontains fins for inducing radial motion. The fins aid in the rotationof actuator piston body 42A which overcomes effects of sand on the valveaction, allows for even wear of the valve 70. It is to be understoodthat the fins of actuator piston body 42A may be spirally shaped asshown in FIG. 18 or spiraled at any angle.

It is also to be understood that the fins or baffles may be positionedanywhere along the body of piston 40 and/or of weight/plunger system 300suitable for inducing, causing, biasing or urging rotation.

FIG. 19A and 19B, are isometric views of piston 40, of the aboveillustration, showing finned actuator piston body 42A with reinforcement42B for the upper valve.

An illustration of such helically aligned grooves, slots, troughs orchannels is shown in FIG. 16, 17A, which is a view of weight/plunger 305taken along FIG. 16 line 17A--17A, and 17B, which is a view ofweight/plunger 305 taken along FIG. 16 line 17B--17B. The descriptionabove is applicable to FIGS. 16, 17A and 17B for like numbers. Referringto FIGS. 16 and 17A there is shown the weight/plunger system 300, whichis like the weight plunger/system 300 of FIG. 12, except for thefollowing changes. First, connector 302 has been replaced by connector302B the surface of which contains a slot, groove or channel 302G, whichmay be spiraled or tapered at any suitable angle or otherwise cut intothe surface of the connector 302B. In addition, fluid flow channels 310are now angled across weight/plunger 305, where fluid flows intoentrance 310A and out of exit 310B. Grooves 302G and channels 310 urgerotation of actuator piston body 42 to overcome effects of sand on thevalve action, strengthen the valve and allow even wear of the valve.

It is to be understood that the flow channels 310 may be cut at anysuitable angle and/or depth that will function to urge rotationactuation piston body 42. It is also to be understood that suchhelically aligned grooves, slots, troughs or channels may be positionedanywhere along the body of piston 40, which may include the actuator 41,actuator piston body 42, and/or weight/plunger system 300, suitable forinducing, causing, biasing or urging rotation.

Additionally, FIG. 16 shows fluid outlet 307C in weight/plunger 305.Fluid outlet 307C keeps the passage clear, aiding in rotation ofactuator piston body 42A.

Referring now to FIG. 17B, there is shown a view of weight plunger 305of FIG. 16 taken along FIG. 16 at line 17B--17B. As shown in FIG. 17B,weight 305 includes sections 305A and 305B, which are connected aroundcoupling end 302A to connector 302 or 302B and extending through guide307B. Weight/plunger 305 fits within the pump housing with one or moreflow channels 310 through weight/plunger 305 with fluid going intoentrance 310A and out of exit 310B.

While one embodiment has been illustrated as having grooves for causingrotation, and another embodiment has been illustrated as having fins forcausing rotation, it should be understood that an apparatus of thepresent invention may include both grooves and fins.

Referring now to FIGS. 20-24 there is provided even another embodimentof the present invention. The description above is applicable to FIGS.20-24 for like numbers. FIG. 20 shows tubular assembly 5 as describedabove, except that conventional standing valve 58 has been replaced bystanding valve 58A of the present invention. Generally, the standingvalve 58A assembly contains a tubular member having one or more guidesthat control movement of ball 56, and the flow of liquid around ball 56.

Referring now to FIG. 21, which is a cross-sectional view of FIG. 20taken along line 21--21, the embodiment of valve 58A as shown includesshallow side ball guides 501, small flow channel 502, large flowchannels 503 and a vortex breaking deep ball guide 504. The ball guides501 and 504 generally comprise structure, either integral to or affixedto the wall of the tubular standing valve, to guide the ball, and whilethe structure of guides 501 and 504 are not to be so limited by thefollowing examples, it may be variously described as a curvalinearsurface, pillar, post, bracket, finger, stud, mast, pedastal,projection, lug, pin, stop, ridge, protrusion, rise, flap, vent, vane,appendage, spindle, leg, lip, spiral, taper, slant or combinationthereof shaped to direct movement and urge a spinning of the ball. It isgenerally desired that ball 56 move to a position that is both away fromstanding valve center 550 yet not impinging on the side of standingvalve 58A, and that creates unequal liquid flow areas around thehorizontal circumference of ball 56. Preferably, these unequal liquidflow areas are such as to urge ball 56 to rotate vertically, that is,around a horizontal axis, i.e., an axis in the horizontal plane.

While not wishing to be limited by theory, applicant believes that inthe prior art standing valves in which the ball was positioned in thecenter, equal flow of liquid around the horizontal circumference of theball would minimize vertical rotation of the ball around a horizontalaxis, and instead would encourage horizontal spinning of the ball aroundthe vertical axis. It is believed that such horizontal spinning of theball increases wear on the ball leading to earlier failure. Applicantbelieves that vertical spinning of the ball would provide cleaning ofthe ball and more favorable wearing of the ball.

While three ball guides, i.e. two ball guides 501 and one ball guide504, are shown in the figures, it must be understood that any suitablenumber of ball guides may be utilized, provided that ball 56 is moved toa suitable position, that is one that is both away from standing valvecenter 550 yet not impinging the side of standing valve 58A, and thatcreates unequal liquid flow areas around the horizontal circumference ofthe ball. It is generally preferred that at least one guide serve tourge ball 56 off center, and that at least one guide serve to preventball 56 from impinging the side of standing valve 58A. Preferably, atleast one ball guide will serve to urge ball 56 off center, and at leastthree ball guides (including the one urging ball 56 off center) serve toprevent ball 56 from impinging the side of standing valve 58A.

In the non-limiting embodiment as shown, ball guide 504 is a taperedridge with its height from the side of the standing valve increasingfrom the bottom to the top of valve 58A, and ball guides 501 are ridgesof constant height. Ball guides 501 and 504 may be of any shape andheight profile provided that ball 56 is moved to a position that is bothaway from standing valve center 550, yet not impinging the side ofstanding valve 58A, and provided that unequal flow areas are createdaround the horizontal circumference of ball 56.

Referring now to FIG. 22, which is a cross-sectional view of FIG. 20taken along line 22--22, and to FIG. 23, which is a cross-sectional viewof FIG. 20 taken alone line 23--23, standing valve 58A includes upperflow channels 526 with a bottom 521 and a top 522, a small ball stop523, an large ball stop 524, and inner diameter of the seat support ring530, upper flow channels 526. Standing valve 58A is seated with aconventional type holddown 520.

Referring to FIG. 24, there is shown another embodiment of standingvalve 58A which includes optional removable liner 527. This removalliner 527 can be inserted into standing valve 58A to allow for the useof different size diameters of ball 56. Removable liner 527 is held inplace by support ring 531 and keeper 528. Removable liner 527 may beprovided with ball guides 501 and 504 as described above, which guidesmay be integral to or affixed to liner 527.

In the operation of standing valve 58A, fluid comes through hold down520 through standing valve seat 57 lifting standing valve ball 56. Asball 56 moves upward, deep ball guide 504 guides ball 56 off centerallowing unequal liquid flow through areas 502 and 503 around thehorizontal circumference of ball 56. Ball 56 rises to small ball stop523 and large ball stop 524. Flow continues up through upper flowchannels 526 with fluid entrance through bottom flow channel 521 andfluid exit through upper flow channel 522.

While not wishing to be limited to theory, the inventor believes thatnew standing valve 58A is designed as a vortex breaker for the suctioninlet of the downhole pump. Placing ball 56 off center will discourageflow reducing horizontal spinning of the ball around its vertical axis,and encourage vertical spin of the ball around an axis in the horizontalplane, which applicant believes cleans the seat during normal operation,cuts vibration and reduces excess wear and provides longer valve life.In addition, the off-center ball, as compared to a centered ball, willallow greater flow through the cage with lesser drop in pressure, whichshould allow for smoother fluid flow into the pump suction. The reduceddrop in pressure additionally results in lower gas break out (i.e.reduces flashing of gas as it enters the pump). The larger flow areas,created by placing the ball off-center, also allow for the moreefficient flow of thicker fluids such as heavy crude. In addition, theshape of ball guide 504 may be varied to induce vertical spin of ball 56around any desired axis in the horizontal plane. The inventor believesthat spin direction may be a factor in the valve's efficiency dependingon whether the valve is used north or south of the equator. In otherwords, the valve could be designed to induce spin in a directiondetermined to increase the efficient flow through the valve when usednorth of the equator and designed to induce spin in the oppositedirection when used south of the equator.

While the illustrative embodiments of the invention have been describedwith particularity, it will be understood that various othermodifications will be apparent to and can be readily made by thoseskilled in the art without departing from the spirit and scope of theinvention. Accordingly, it is not intended that the scope of the claimsappended hereto be limited to the examples and descriptions set forthherein but rather that the claims be construed as encompassing all thefeatures of patentable novelty which reside in the present invention,including all features which would be treated as equivalents thereof bythose skilled the art to which this invention pertains.

I claim:
 1. A standing valve comprising:(a) a hollow tubular memberhaving an interior wall defining an internal cross-sectional area, andhaving a vertical center line; (b) a valve seat mounted within thetubular member, having a seating passage with a seating cross-sectionalarea; (c) a ball positioned within the tubular member above the valveseat; (d) at least one first ball guide radially extending within thehollow tubular member which guides the ball to a position such that theball is not centered on the center line, and such that unequal liquidflow areas are created around the horizontal circumference of the ball;(e) at least one second ball guide radially extending within the hollowtubular member, wherein the second ball guide is positioned to operatewith the first ball guide to prevent the ball from impinging upon thehollow tubular member. wherein the standing valve is closed by the ballbeing seated on the valve seat, and opened by an increase in pressurefrom below or a vacuum from above unseating the ball from the valveseat.
 2. The standing valve of claim 1 wherein the ball guide is astructure extending inwardly from the interior wall of the hollowtubular member.
 3. The standing valve of claim 2 wherein the structurecomprises at least one of curvalinear surface, pillar, post, bracket,finger, stud, mast, pedastal, projection, lug, pin, stop, ridge,protrusion, rise, flap, vent, vane, appendage, spindle, leg, lip,spiral, taper or slant.
 4. The standing valve of claim 1 wherein theball guide is designed to induce the ball to spin around a desired axis.5. The standing valve of claim 1 further comprising(e) a removable linerlocated within the hollow tubular member wherein the ball guide islocated within the removable liner.
 6. A ball and seat valve assemblycomprising:(a) a first hollow tubular member having an internalcross-sectional area; (b) a valve seat mounted within the first tubularmember, having a seating passage with a seating cross-sectional area;(c) a ball positioned within the first tubular member above the valveseat; (d) a piston movably mounted within the first tubular member belowthe valve seat, comprising an actuator for engaging the ball through thepassage while the ball is seated on the seat, and comprising a sealingmember with a sealing cross-sectional area for sealing the first tubularmember below the valve seat across the entire internal cross-sectionalarea of the tubular member, wherein the sealing cross-sectional area isgreater than the seating cross-sectional area; wherein the ball and seatvalve is closed by the ball being seated on the seat valve, and openedby an increase in fluid pressure below the piston acting upon thesealing cross-sectional area causing the piston to rise and engage theball with the actuator and thereby unseat the ball; and (e) A standingvalve comprising:(i) a second hollow tubular member having an internalcross-sectional area, and having a vertical center line; (ii) a secondvalve seat mounted within the second tubular member, having a seatingpassage with a seating cross-sectional area; (iii) a second ballpositioned within the second tubular member above the second valve seat;(iv) at least one first ball guide radially extending within the secondtubular member which guides the ball to a position such that the ball isnot centered on the center line, and such that unequal liquid flow areasare created around the horizontal circumference of the ball; (v) atleast one second ball guide radially extending within the second hollowtubular member, wherein the second ball guide is positioned to operatewith the first ball guide to prevent the ball from impinging upon thesecond hollow tubular member;wherein the standing valve is closed by thesecond ball being seated on the second valve seat, and opened by anincrease in pressure from below or a vacuum from above unseating thesecond ball from the second valve seat.
 7. The standing valve of claim 6wherein the ball guide is a structure extending inwardly from theinterior wall of the hollow tubular member.
 8. The standing valve ofclaim 6 wherein the ball guide is designed to induce the ball to spinaround a desired axis.
 9. The apparatus of claim 6 furthercomprising:(f) A weight connected to and positioned below the piston.10. The apparatus of claim 6 further comprising:(g) A rotationalinducing mechanism connected to the piston for urging rotation of thepiston as it rises and engages the ball.
 11. A ball and seat valveassembly comprising:(a) a first hollow tubular member; (b) a valve seatmounted within the first tubular member, having a seating passage; (c) aball positioned within the first tubular member above the valve seat,and having a vertical axis through its center; (d) a piston movablymounted within the first tubular member below the valve seat, comprisingan actuator for engaging the ball through the passage while the ball isseated on the seat, and comprising a sealing member for sealing thefirst tubular member below the valve seat, wherein the actuator isshaped to engage the ball asymetrically with respect to the verticalaxis of the ball; wherein the ball and seat valve is closed by the ballbeing seated on the seat valve, and opened by an increase in fluidpressure below the piston causing the piston to rise and asymetricallyengage the ball with the actuator and thereby unseat the ball; and (e) Astanding valve comprising:(i) a second hollow tubular member having aninternal cross-sectional area, and having a vertical center line; (ii) asecond valve seat mounted within the second tubular member, having aseating passage with a seating cross-sectional area; (iii) a second ballpositioned within the second tubular member above the second valve seat;(iv) at least one first ball guide radially extending within the secondtubular member which guides the ball to a position such that the ball isnot centered on the center line, and such that unequal liquid flow areasare created around the horizontal circumference of the ball; (v) atleast one second ball guide radially extending within the second hollowtubular member, wherein the second ball guide is positioned to operatewith the first ball guide to prevent the ball from impinging upon thesecond hollow tubular member;wherein the standing valve is closed by thesecond ball being seated on the second valve seat, and opened by anincrease in pressure from below or a vacuum from above unseating thesecond ball from the second valve seat.
 12. The standing valve of claim11 wherein the ball guide comprises at least one of curvalinear surface,pillar, post, bracket, finger, stud, mast, pedastal, projection, lug,pin, stop, ridge, protrusion, rise, flap, vent, vane, appendage,spindle, leg, lip, spiral, taper or slant.
 13. The standing valve ofclaim 11 further comprising(e) a removable liner located within thehollow tubular member wherein the ball guide is located within theremovable liner.
 14. The apparatus of claim 11 further comprising:(f) Aweight connected to and positioned below the piston.
 15. The apparatusof claim 11 further comprising:(g) A rotational inducing mechanismconnected to the piston for urging rotation of the piston as it risesand engages the ball.
 16. A ball and seat valve assembly comprising:(a)a valve seat having a seating passage with a seating cross-sectionalarea, and having a top and a bottom; (b) a ball positioned above thevalve seat; (c) a first hollow tubular member mounted to the bottom ofthe valve seat, and having an internal cross-sectional area; (d) apiston movably mounted within the first tubular member, comprising anactuator for engaging the ball through the passage while the ball isseated on the seat, and comprising a sealing member with a sealingcross-sectional area for sealing the first tubular member below thevalve seat across the entire internal cross-sectional area of the firsttubular member, wherein the sealing cross-sectional area is greater thanthe seating cross-sectional area; wherein an increase in fluid pressurebelow the piston acting upon the sealing cross-sectional area causes thepiston to rise and engage the ball with the actuator and thereby unseatthe ball; and (e) A standing valve comprising:(i) a second hollowtubular member having an internal cross-sectional area, and having avertical center line; (ii) a second valve seat mounted within the secondtubular member, having a seating passage with a seating cross-sectionalarea; (iii) a second ball positioned within the second tubular memberabove the second valve seat; (iv) at least one first ball guide radiallyextending within the second tubular member which guides the ball to aposition such that the ball is not centered on the center line, and suchthat unequal liquid flow areas are created around the horizontalcircumference of the ball; (v) at least one second ball guide radiallyextending within the second hollow tubular member, wherein the secondball guide is positioned to operate with the first ball guide to preventthe ball from impinging upon the second hollow tubular member;whereinthe standing valve is closed by the second ball being seated on thesecond valve seat, and opened by an increase in pressure from below or avacuum from above unseating the second ball from the second valve seat.17. The standing valve of claim 16 wherein the ball guide is a structureextending inwardly from the interior wall of the hollow tubular member.18. The standing valve of claim 16 wherein the ball guide is designed toinduce the ball to spin around a desired axis.
 19. The apparatus ofclaim 16 further comprising:(f) A weight connected to and positionedbelow the piston.
 20. The apparatus of claim 16 further comprising:(g) Arotational inducing mechanism connected to the piston for urgingrotation of the piston as it rises and engages the ball.
 21. A ball andseat valve assembly comprising:(a) a valve seat having a seatingpassage, and having a top and a bottom; (b) a ball positioned above thevalve seat, and having a vertical axis through its center; (c) a firsthollow tubular member mounted to the bottom of the valve seat; (d) apiston movably mounted within the first tubular member, comprising anactuator for engaging the ball through the passage while the ball isseated on the seat, and comprising a sealing member for sealing thefirst tubular member, wherein the actuator is shaped to engage the ballasymetrically with respect to the vertical axis of the ball; wherein anincrease in fluid pressure below the piston causes the piston to riseand engage the ball with the actuator and thereby unseat the ball; and(e) A standing valve comprising:(i) a second hollow tubular memberhaving an internal cross-sectional area, and having a vertical centerline; (ii) a second valve seat mounted within the second tubular member,having a seating passage with a seating cross-sectional area; (iii) asecond ball positioned within the second tubular member above the secondvalve seat; (iv) at least one first ball guide radially extending withinthe second tubular member which guides the ball to a position such thatthe ball is not centered on the center line, and such that unequalliquid flow areas are created around the horizontal circumference of theball; (v) at least one second ball guide radially extending within thesecond hollow tubular member, wherein the second ball guide ispositioned to operate with the first ball guide to prevent the ball fromimpinging upon the second hollow tubular member;wherein the standingvalve is closed by the second ball being seated on the second valveseat, and opened by an increase in pressure from below or a vacuum fromabove unseating the second ball from the second valve seat.
 22. Thestanding valve of claim 21 wherein the ball guide comprises at least oneof curvalinear surface, pillar, post, bracket, finger, stud, mast,pedastal, projection, lug, pin, stop, ridge, protrusion, rise, flap,vent, vane, appendage, spindle, leg, lip, spiral, taper or slant. 23.The standing valve of claim 21 further comprising(e) a removable linerlocated within the hollow tubular member wherein the ball guide islocated within the removable liner.
 24. The apparatus of claim 21further comprising:(f) A weight connected to and positioned below thepiston.
 25. The apparatus of claim 21 further comprising:(g) Arotational inducing mechanism connected to the piston for urgingrotation of the piston as it rises and engages the ball.
 26. A ball andseat valve assembly comprising:(a) an upper hollow tubular member,having a bottom end; (b) a valve seat mounted within the upper tubularmember, having a seating passage with a seating cross-sectional area;(c) a ball positioned within the upper tubular member above the valveseat; (d) a lower hollow tubular member, having an internalcross-sectional area, and having a top end, wherein the top end of thelower tubular member is connected to the bottom end of the upper tubularmember; (e) a piston movably mounted within the lower tubular member,comprising an actuator for engaging the ball through the passage whilethe ball is seated on the seat, and comprising a sealing member with asealing cross-sectional area for sealing the lower tubular member acrossthe entire internal cross-sectional area of the lower tubular member,wherein the sealing cross-sectional area is greater than the seatingcross-sectional area; wherein the ball and seat valve is closed by theball being seated on the seat valve, and opened by an increase in fluidpressure below the piston acting upon the sealing cross-sectional areacausing the piston to rise and engage the ball with the actuator andthereby unseat the ball; and (f) A standing valve comprising:(i) asecond hollow tubular member having an internal cross-sectional area,and having a vertical center line; (ii) a second valve seat mountedwithin the second tubular member, having a seating passage with aseating cross-sectional area; (iii) a second ball positioned within thesecond tubular member above the second valve seat; (iv) at least onefirst ball guide radially extending within the second tubular memberwhich guides the ball to a position such that the ball is not centeredon the center line, and such that unequal liquid flow areas are createdaround the horizontal circumference of the ball;(v) at least one secondball guide radially extending within the second hollow tubular member,wherein the second ball guide is positioned to operate with the firstball guide to prevent the ball from impinging upon the second hollowtubular member;wherein the standing valve is closed by the second ballbeing seated on the second valve seat, and opened by an increase inpressure from below or a vacuum from above unseating the second ballfrom the second valve seat.
 27. The standing valve of claim 26 whereinthe ball guide is a structure extending inwardly from the interior wallof the hollow tubular member.
 28. The standing valve of claim 26 whereinthe ball guide is designed to induce the ball to spin around a desiredaxis.
 29. The apparatus of claim 26 further comprising:(g) A weightconnected to and positioned below the piston.
 30. The apparatus of claim26 further comprising:(h) A rotational inducing mechanism connected tothe piston for urging rotation of the piston as it rises and engages theball.
 31. A ball and seat valve assembly comprising:(a) an upper hollowtubular member, having a bottom end; (b) a valve seat mounted within theupper tubular member, having a seating passage; (c) a ball positionedwithin the upper tubular member above the valve seat, and having avertical axis through its center; (d) a lower hollow tubular member, andhaving a top end, wherein the top end of the lower tubular member isconnected to the bottom end of the upper tubular member; (e) a pistonmovably mounted within the lower tubular member, comprising an actuatorfor engaging the ball through the passage while the ball is seated onthe seat, and comprising a sealing member for sealing the lower tubularmember, wherein the actuator is shaped to engage the ball asymetricallywith respect to the vertical axis of the ball; wherein the ball and seatvalve is closed by the ball being seated on the seat valve, and openedby an increase in fluid pressure below the piston causing the piston torise and asymetrically engage the ball with the actuator and therebyunseat the ball; and (f) A standing valve comprising:(i) a second hollowtubular member having an internal cross-sectional area, and having avertical center line; (ii) a second valve seat mounted within the secondtubular member, having a seating passage with a seating cross-sectionalarea; (iii) a second ball positioned within the second tubular memberabove the second valve seat; (iv) at least one first ball guide radiallyextending within the second tubular member which guides the ball to aposition such that the ball is not centered on the center line, and suchthat unequal liquid flow areas are created around the horizontalcircumference of the ball; (v) at least one second ball guide radiallyextending within the second hollow tubular member, wherein the secondball guide is positioned to operate with the first ball guide to preventthe ball from impinging upon the second hollow tubular member;whereinthe standing valve is closed by the second ball being seated on thesecond valve seat, and opened by an increase in pressure from below or avacuum from above unseating the second ball from the second valve seat.32. The standing valve of claim 31 wherein the ball guide comprises atleast one of curvalinear surface, pillar, post, bracket, finger, stud,mast, pedastal, projection, lug, pin, stop, ridge, protrusion, rise,flap, vent, vane, appendage, spindle, leg, lip, spiral, taper or slant.33. The standing valve of claim 31 further comprising(e) a removableliner located within the hollow tubular member wherein the ball guide islocated within the removable liner.
 34. The apparatus of claim 31further comprising:(g) A weight connected to and positioned below thepiston.
 35. The apparatus of claim 31 further comprising:(h) Arotational inducing mechanism connected to the piston for urgingrotation of the piston as it rises and engages the ball.
 36. A pumpassembly comprising:(a) a tubular pump barrel providing a workingchamber; (b) a movable tubular housing positioned for longitudinalreciprocal movement in the housing working chamber; (c) a travelingvalve assembly positioned in the chamber and connected to and movablewith the housing, comprising a valve seat having a seating passage witha seating cross-sectional area, and comprising a ball positioned abovethe valve seat; (d) a hollow tubular actuator assembly positioned withinthe chamber, having an internal cross-sectional area, and having a topend, wherein the top end of the tubular member is connected to thetraveling valve assembly; (e) a piston movably mounted within theactuator assembly, comprising an actuator for engaging the ball throughthe passage while the ball is seated on the seat, and comprising asealing member with a sealing cross-sectional area for sealing theactuator assembly across the entire internal cross-sectional area of theactuator assembly, wherein the sealing cross-sectional area is greaterthan the seating cross-sectional area; (f) A standing valvecomprising:(i) a second hollow tubular member having an internalcross-sectional area, and having a vertical center line; (ii) a secondvalve seat mounted within the second tubular member, having a seatingpassage with a seating cross-sectional area; (iii) a second ballpositioned within the second tubular member above the second valve seat;(iv) at least one first ball guide radially extending within the secondtubular member which guides ball to a position such that the ball is notcentered on the center line, and such that unequal liquid flow areas arecreated around the horizontal circumference of the ball; (v) at leastone second ball guide radially extending within the second hollowtubular member, wherein the second ball guide is positioned to operatewith the first ball guide to prevent the ball from impinging upon thesecond hollow tubular member;wherein the standing valve is closed by thesecond ball being seated on the second valve seat, and opened by anincrease in pressure from below or a vacuum from above unseating thesecond ball from the second valve seat. wherein upward movement of thehousing is effective to draw liquid through the standing valve assembly,subsequent downward movement of the housing is effective to increase theliquid pressure between the standing valve and the piston causing thepiston to rise and engage the traveling valve assembly ball with theactuator and thereby unseat the ball.
 37. The standing valve of claim 36wherein the ball guide is a structure extending inwardly from theinterior wall of the hollow tubular member.
 38. The standing valve ofclaim 36 wherein the ball guide is designed to induce the ball to spinaround a desired axis.
 39. The apparatus of claim 36 furthercomprising:(h) A weight connected to and positioned below the piston.40. The apparatus of claim 36 further comprising:(i) A rotationalinducing mechanism connected to the piston for urging rotation of thepiston as it rises and engages the ball.
 41. A pump assemblycomprising:(a) a tubular pump barrel providing a working chamber; (b) amovable housing positioned for longitudinal reciprocal movement in theworking chamber; (c) a traveling valve assembly positioned in thechamber and connected to and movable with the housing, comprising avalve seat having a seating passage, and comprising a ball positionedabove the valve seat, wherein the ball has a vertical axis through itscenter; (d) a hollow tubular actuator member positioned within thechamber, having a top end, wherein the top end of the tubular member isconnected to the traveling valve assembly; (e) a piston movably mountedwithin the actuator, comprising an actuator suitable for asymetricallyengaging the ball through the passage while the ball is seated on theseat, and comprising a sealing member for sealing the actuator; (f) Astanding valve comprising:(i) a second hollow tubular member having aninternal cross-sectional area, and having a vertical center line; (ii) asecond valve seat mounted within the second tubular member, having aseating passage with a seating cross-sectional area; (iii) a second ballpositioned within the second tubular member above the second valve seat;(iv) at least one first ball guide radially extending within the secondtubular member which guides the ball to a position such that the ball isnot centered on the center line, and such that unequal liquid flow areasare created around the horizontal circumference of the ball; (v) atleast one second ball guide radially extending within the second hollowtubular member, wherein the second ball guide is positioned to operatewith the first ball guide to prevent the ball from impinging upon thesecond hollow tubular member;wherein the standing valve is closed by thesecond ball being seated on the second valve seat, and opened by anincrease in pressure from below or a vacuum from above unseating thesecond ball from the second valve seat; wherein upward movement of thehousing is effective to draw liquid through the standing valve assembly,subsequent downward movement of the housing is effective to increase theliquid pressure between the standing valve and the piston causing thepiston to rise and asymetrically engage the traveling valve assemblyball with the actuator and hereby unseat the ball.
 42. The standingvalve of claim 41 wherein the ball guide comprises at least one ofcurvalinear surface, pillar, post, bracket, finger, stud, mast,pedastal, projection, lug, pin, stop, ridge, protrusion, rise, flap,vent, vane, appendage, spindle, leg, lip, spiral, taper or slant. 43.The standing valve of claim 41 further comprising(e) a removable linerlocated within the hollow tubular member wherein the ball guide islocated within the removable liner.
 44. The apparatus of claim 41further comprising:(h) A weight connected to and positioned below thepiston.
 45. The apparatus of claim 41 further comprising:(i) Arotational inducing mechanism connected to the piston for urgingrotation of the piston as it rises and engages the ball.